CN106715925B - The driving device of hydrostatic - Google Patents

The driving device of hydrostatic Download PDF

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Publication number
CN106715925B
CN106715925B CN201580049475.2A CN201580049475A CN106715925B CN 106715925 B CN106715925 B CN 106715925B CN 201580049475 A CN201580049475 A CN 201580049475A CN 106715925 B CN106715925 B CN 106715925B
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CN
China
Prior art keywords
pressure
valve
swept volume
hydraulic press
driving device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201580049475.2A
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Chinese (zh)
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CN106715925A (en
Inventor
M.马斯特
P.L.赫南德斯拉德拉
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Robert Bosch GmbH
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Robert Bosch GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N7/00—Starting apparatus having fluid-driven auxiliary engines or apparatus
    • F02N7/08—Starting apparatus having fluid-driven auxiliary engines or apparatus the engines being of rotary type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/08—Prime-movers comprising combustion engines and mechanical or fluid energy storing means
    • B60K6/12—Prime-movers comprising combustion engines and mechanical or fluid energy storing means by means of a chargeable fluidic accumulator
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2246—Control of prime movers, e.g. depending on the hydraulic load of work tools
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/027—Installations or systems with accumulators having accumulator charging devices
    • F15B1/033—Installations or systems with accumulators having accumulator charging devices with electrical control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/08—Prime-movers comprising combustion engines and mechanical or fluid energy storing means
    • B60K6/12—Prime-movers comprising combustion engines and mechanical or fluid energy storing means by means of a chargeable fluidic accumulator
    • B60K2006/126—Prime-movers comprising combustion engines and mechanical or fluid energy storing means by means of a chargeable fluidic accumulator the hydraulic accumulator starts the engine
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2400/00—Special features of vehicle units
    • B60Y2400/46—Engine start hydraulic or electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20523—Internal combustion engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40523—Flow control characterised by the type of flow control means or valve with flow dividers
    • F15B2211/4053—Flow control characterised by the type of flow control means or valve with flow dividers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/411—Flow control characterised by the positions of the valve element the positions being discrete
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/526—Pressure control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6343—Electronic controllers using input signals representing a temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The driving device for disclosing hydrostatic, particularly for starting the internal combustion engine.The driving device includes：Hydraulic press, the hydraulic press can be adjusted from maximum positive swept volume by zero swept volume to maximum negative swept volume by means of the regulating device of hydraulic pressure in its swept volume, which can be run as pumping using positive swept volume and can be run as motor using negative swept volume；At least one high pressure accumulator is capable of supply that the hydraulic press from the pressure line moved towards between the compression fittings and the high pressure accumulator of the hydraulic press is passed through in the high pressure accumulator for the operation as hydraulic motor using pressure medium；Memory shut-off valve with first position and the second position, the memory shut-off valve are arranged in the pressure line and make the portion that fluidly connects from the high pressure accumulator towards hydraulic press open in first position and end in the second position by the memory shut-off valve；And the control unit of electronics, the signal dependent on the control unit can actuate the memory shut-off valve.The driving device of the hydrostatic should such moulding：So that the component of hydraulic press is not subjected to high abrasion, and realize from the quick reset in the region of negative swept volume.This point is achieved in：I.e., when hydraulic press is adjusted from negative swept volume towards positive swept volume, the controller of the electronics is then given the signal for being switched to the memory shut-off valve from first position in the second position so that the memory shut-off valve is just switched in zero swept volume or the positive swept volume of the hydraulic press in the second position.

Description

The driving device of hydrostatic
Technical field
The present invention relates to a kind of driving device of hydrostatic, especially it is arranged for starting internal combustion engine, especially diesel oil Motor.
Background technology
Known a kind of driving device of hydrostatic from 2012/125798 A1 of WO, with hydraulic press, the hydraulic press Start internal combustion engine in the operation as hydraulic motor and loads hydropneumatic high pressure accumulator in the operation as pump And the consumable component of other hydraulic pressure can be supplied using pressure medium.
The hydraulic press by means of the regulating device of hydraulic pressure in its swept volume from maximum positive swept volume through zero passage Swept volume can adjust maximum negative swept volume, wherein for positive swept volume, it is understood that there may be pump operation, and it is right In negative swept volume, it is understood that there may be motor operation.Here, the swept volume is pressure medium amount, the pressure medium amount for The revolution of each of transmission shaft from the hydraulic press feed or is swallowed.For the operation as hydraulic motor, stored from high pressure Pass through pressure line in device（The pressure line moves towards between the compression fittings and high pressure accumulator of the hydraulic press）Utilize pressure Power media is capable of supply that the hydraulic press.Memory shut-off valve with first position and the second position is arranged in the pressure line Lu Zhong, wherein the memory shut-off valve from the high pressure accumulator towards hydraulic press fluidly connecting portion in first position It opens and ends in the second position.The signal of controller dependent on electronics can actuate the memory shut-off valve.
Usually there is the regulating device of the hydraulic pressure of the swept volume of machine for hydrostatic one or more adjust to live Plug（Adjusting cavity is abutted to the regulating piston）With at least one return spring, make in default institute under the action of the return spring The hydraulic press is adjusted onto predetermined swept volume when stating the pressure-loaded of adjusting cavity.
Invention content
The targeted task of the present invention is, establishes a kind of driving device for starting the hydrostatic of internal combustion engine, Wherein, it can rapidly and without the excess load of component be adjusted from the adjustment region with negative swept volume Hydraulic press.
This task is solved by a kind of driving device of hydrostatic, the driving device particularly for start internal combustion engine, The driving device has hydraulic press, and the hydraulic press is by means of the regulating device of hydraulic pressure from maximum in the swept volume of the hydraulic press Positive swept volume can adjust maximum negative swept volume by zero swept volume, which utilizes positive swept volume energy It is enough used as pump operation and can have at least one high pressure to deposit as motor operation, the driving device using negative swept volume Reservoir, for the operation as hydraulic motor, by the compression fittings and the height in the hydraulic press from the high pressure accumulator The pressure line moved towards between pressure memory can utilize pressure medium to supply the hydraulic press, and the driving device, which has, to be carried The memory shut-off valve of first position and the second position, the memory shut-off valve are arranged in the pressure line and by this Memory shut-off valve makes the portion that fluidly connects from the high pressure accumulator towards hydraulic press be opened simultaneously in the first position And end in the second position, and the driving device has the control unit of electronics, dependent on the control unit Signal can operate the memory shut-off valve, wherein when adjusting hydraulic press from negative swept volume towards positive swept volume, The control unit of the electronics is provided at this time for the memory shut-off valve to be switched to from first position in the second position Signal so that the memory shut-off valve is just cut in the case of zero swept volume of the hydraulic press or positive swept volume It changes in the second position.
In the driving device of hydrostatic according to the present invention, hydraulic press is being held from negative swept volume towards positive work When product is adjusted, the controller of the electronics from first position by the memory shut-off valve then just given for being switched to the Signal in two positions so that memory shut-off valve ability in zero swept volume or the positive swept volume of the hydraulic press It is switched in the second position.It therefore ensures that, in the time（From maximum negative swept volume to the tune of zero swept volume Section requires the time）Period, there is also the compression fittings from the hydraulic press to fluidly connect portion towards high pressure accumulator.Thus It is ensured that, pressure line is not evacuated and hole thus do not occur by the hydraulic press, which can result in the damage of component Wound.Respectively according to the type of adjustment equipment, the pressure in pressure line can be also used at this time：It is adjusted using pressure-loaded The pressure-loaded of chamber, the adjusting cavity acts as in the meaning being adjusted from negative swept volume towards the direction of zero swept volume With, to can not only use the adjustment equipment return spring power, and can use for by the hydraulic press from The extruding force resetted in region with negative swept volume.
The advantageous structural scheme of the present invention can be found out from dependent claims.
It is known to the hydraulic press adjusted, it includes being abutted to the first tune which, which has regulating device, the regulating device, Save the first adjusting cavity of piston（For the adjusting cavity, it can control to facilitate by valve gear and hold towards maximum negative work The influent stream for the pressure medium that long-pending direction is adjusted and drainage can be controlled）, be abutted to the second regulating piston second adjust Save chamber（The adjusting cavity is fluidly connected with the pressure line and the adjusting cavity is in the direction towards maximum negative swept volume Adjusting in reduce and increase in the adjusting in the direction towards maximum positive swept volume）And return spring, the return bullet It works in the direction of spring towards maximum positive swept volume.When adjusting cavity is by from pressure off-load, such hydraulic press is conditioned Onto maximum positive swept volume.By the way that pressure medium is abutted to the first regulating piston into flowing to（The effect of the regulating piston Face is more than the acting surface of second regulating piston）In the adjusting cavity at place, the hydraulic press can be held from maximum positive work Product is directly adjusted towards maximum negative swept volume by zero swept volume.Herein, thus in second adjusting cavity always In the presence of the pressure present in the pressure line, to during the hydraulic press is resetted from motor operation, be maintained When pressure in the pressure line, when without other control unit, by valve so that a kind of extruding force contributes to this It resets.
The valve gear of influent stream and drainage for controlling the pressure medium from the first adjusting cavity preferably includes control valve, By the control valve, the adjusting for the negative swept volume towards the first adjusting cavity, independent of the working joint, from pressure The hydraulic press can be supplied in medium source, especially from high pressure accumulator using pressure medium.
Operation for the hydraulic press as pump, the valve gear include the adjuster of hydraulic pressure, which is additional to institute It states control valve and exists.For with hydraulic pressure adjuster and with the mating reaction of high pressure accumulator, the control valve is 3/2 tunnel Valve, the control valve carry the first connector（The connector is fluidly connected with the adjusting pressure output end of the adjuster of the hydraulic pressure）And And carry the second connector（The connector is fluidly connected with the pressure medium source）And carry third connector（The connector with it is described First adjusting cavity is connected）, and wherein, the control valve has first position（In the first position, the output end and One input terminal is fluidly connected and the second input terminal ends）And the second position, in the second position, the output end and Two input terminals are connected and first input end ends.The adjuster of the hydraulic pressure is in the first position of the control valve as a result, The swept volume of the hydraulic press can be influenced, and is not acted in the second position of the control valve.
In particular, the adjuster of the hydraulic pressure is load-sensing（LS）Regulating valve, the regulating valve are flowed into pressure medium to institute It states in the meaning of the first adjusting cavity of regulating device by the pressure-loaded in the pressure line and in pressure medium from institute It states in the meaning flowed out in the first adjusting cavity by adjustment spring and being present in LS connectors（X）The LS control pressures at place load, and Wherein, also LS control pressures are given to the load-sensing in the negative swept volume of the hydraulic press（LS）The LS of regulating valve Connector.By correspondingly selecting the LS control pressures, at least LS control pressures signal（The LS control pressure signals are previously given The LS control pressures）, then can be accomplished that, on the one hand also rapidly adjust institute from the region with negative swept volume State hydraulic press, but simultaneously non-regulated until maximum positive swept volume.It hereby is obtained that, the internal combustion engine is passing through the hydraulic pressure Machine is not loaded optionally and rapidly be can speed up after starting and run in idler revolutions.
Advantageously, the load-sensing is loaded with using LS control pressures（LS）Regulating valve, and the control valve is also In its second position.As long as the control valve is also located in its second position, then the load holding of the LS regulating valves does not have Have an impact, because its control output end is not connected with first adjusting cavity.Preferably, the LS control pressures even approach Memory pressure, as long as control valve occupies its second position.Then in the instantaneous of the switching of control valve, suitable LS is had existed Control pressure, and need not also fill control circuit or so that the moveable control volume of valve makes larger stroke.
Advantageously, the LS control pressures are for example with the pressure equivalent of adjustment spring less than the pressure in the pressure line Power（When the hydraulic press reaches zero swept volume when back swinging from maximum negative swept volume）, to the hydraulic press Be conditioned by zero swept volume, but simultaneously non-regulated until maximum positive swept volume.The LS control pressures with it is accurate Value（From having obtained the value in the difference of the pressure equivalent of the adjustment spring and the pressure in the pressure line）Deviation It is balanced in the case of the swept volume only slightly deviateed from zero swept volume, especially after swept volume hands over zero, The hydraulic storage is detached with the hydraulic press, and in the pressure in the pressure line of smaller hydraulic capacity Must also just it change.
Preferably, when the control valve is also located in its second position, LS control pressures have been given to described negative Carry induction（LS）The LS connectors of regulating valve, wherein the LS control pressures with fixed pressure difference, store first in the high pressure Pressure in device is hereinafter, follow the memory pressure of decline, and wherein, at least described previously given LS control pressures LS control pressure signals are kept constant, when in the control valve being converted from its second position to its first position.Herein can Happens is that the LS control pressures are not corresponded to by the previously given value of LS control pressure signals, because from memory pressure The LS control pressures signal is derived, and in the position of the fluid path between high pressure accumulator and hydraulic press（In the position Place is set, control oil is taken out, for generating the LS control pressures）The pressure at place, due in the high pressure accumulator and hydraulic pressure Between machine based on the fluid flowing the pressure loss and be less than desired LS control pressures.Real-time LS control pressures are but Such pressure can not be higher than：The LS control pressures are generated from the pressure.Thus then the LS control pressures with Pressure in fluid path further decreases, although the LS control pressures signal is kept constant.If in the control valve What is switched is instantaneous, and the real-time LS control pressures are equal to or are less than with the pressure equivalent less than the adjustment spring The pressure being applied on negative direction in the LS regulating valves, then this LS regulating valve be located in such position：Wherein, described One adjusting cavity is connected with storage tank.The hydraulic press is then soon from the region of negative swept volume towards the side of zero swept volume To adjusting.If due to the instantaneous special situation of the switching in the control valve, the real-time LS control pressures are with big It is less than the pressure being applied in the reverse direction in the LS regulating valves in the pressure equivalent of the adjustment spring, then this LS is adjusted Valve is also located at first in such position：Wherein, first adjusting cavity is connected with pressure line.The hydraulic press then slightly It is micro- to be maintained in motor operation more long.Decline in the pressure line and the pressure in high pressure accumulator, to the LS Regulating valve enters in such position：Wherein, the first adjusting cavity is towards storage tank off-load.
Show that when the fixed difference between memory pressure and LS control pressure signals be the LS regulating valves When about 1.75 times of the pressure equivalent of adjustment spring so big, the hydraulic press rapidly back swing and will not towards compared with Big positive swept volume is shown.
It is possible that the drive system of the hydrostatic only relies upon the rotating speed of hydraulic press and in high pressure accumulator Pressure controls, and using pressure recorder detects the pressure.
At this moment more accurate control and more quick reset show as feasible：It is useful for that is, matching when the hydraulic press When the logger of swept volume, and after being switched to control valve in first position from the second position, the LS controls pressure The size of power, the size of at least described LS control pressures signal dependent on the memory pressure and negative swept volume size or Person bears the change of swept volume come when determining.
If for swept volume, there are loggers, and control valve is being switched to it in first position from the second position Afterwards, namely after starting process terminates, the memory shut-off valve is sized to dependent on detected swept volume It is switched in the second position from first position.
Description of the drawings
The embodiment of the driving device of hydrostatic according to the present invention is shown in the accompanying drawings.According to the unique of attached drawing Figure illustrates the present invention in further detail now.
Fig. 1 shows the line map of the embodiment.
Specific implementation mode
It is also used in Fig. 1 as the driving device of hydrostatic shown in line map in addition to being used to start diesel motor Operation and for actuate mobile work machines equipment and include the manoeuvre portion 1 of hydrostatic and the consumable component 2 of other hydraulic pressure. The driving device combination diesel motor 4 uses, and the rotating speed of the diesel motor passes through the revolution speed sensing that does not show in further detail Device detects and the bent axle of the driving device 6 is coupled to the transmission shaft 8 of hydraulic press 10, which passes through in its swept volume Zero passage swept volume can be adjusted between positive swept volume and negative swept volume, which is configured in oblique disk structure form In axial piston machine.Here, the swash plate is stroke control element, which passes through its position, it is determined that The swept volume of hydraulic press between maximum positive swept volume and maximum negative swept volume.Such axial piston machine is also referred to as For the axial piston machine that can be swung completely.Its shell 12 has storage tank connector T and compression fittings P, wherein the two connectors T and P It enduringly and is clearly arranged to high pressure and storage tank pressure.It is described can completely oscillatory be accomplished that, be maintained pump transport Positive swept volume in row（Wherein, which draws pressure medium and provides from storage tank 13 by storage tank connector T Into compression fittings P）When rotation direction in the case of, and in motor operation（In the motor operation, pressure medium is from pressure Power media source is flowed towards the compression fittings P, which flows out to by the storage tank connector T in storage tank 13）In When negative swept volume, hydraulic press 10 is run.
Pressure lines 14 and the manoeuvre portion 1 and other consumable component 2 and and high pressure of the compression fittings P by branch Memory 16 is connected.In addition, the pressure line 14 has branch 18.Below, it should discuss high pressure accumulator respectively, i.e., Make as shown multiple high pressure accumulators be connected in parallel to each other.
The branch 18 and on the other hand between the manoeuvre portion 1 and other consumable component 2 on the one hand, be provided with by It is configured to the consumable component shut-off valve 20 of 2/2 way reversing valve.It by spring through in the base position of preload, by the manoeuvre portion 1 It is connected with the compression fittings of hydraulic press 10 and high pressure accumulator 16 with other consumable component 2, and it is in the on-position through actuating The pressure line 14 is directly ended towards the manoeuvre portion 1 and consumable component 2.
Pressure at the compression fittings P is hereinafter referred to as pump pressure.The pressure（Even if being deposited in hydraulic press and high pressure Interconnecting piece between reservoir opens wide）Memory pressure can be deviated from based on flow losses.
Between the branch 18 and the high pressure accumulator 16, memory shut-off valve is provided in pressure line 14 22, the memory shut-off valve is in by spring through the base position of preload along from high pressure accumulator 16 towards 18 He of branch The flow direction of hydraulic press 10 is ended, and the memory shut-off valve makes in the on-position through actuating in the height The portion of fluidly connecting between memory 16 and hydraulic press 10 is pressed to open wide.In the base position of the memory shut-off valve 22, from The pressure medium flow of the hydraulic press 10 to high pressure accumulator 16 is feasible.
The hydraulic press 10 for being configured to the axial piston machine swung completely possesses regulating device, and the regulating device is basic It is upper that there is the first regulating piston 26, the regulating piston to react on the second regulating piston 28 and return spring 29.Described first adjusts The acting surface for saving piston 26 is more than the acting surface of second regulating piston 28.The regulating piston 26 defines adjusting cavity 30. Ground is controlled by valve gear 31, pressure medium can be provided to adjusting cavity 30 by chamber connector 32 and from the adjusting cavity 30 Discharge.Second regulating piston 28 defines adjusting cavity 33, which enduringly flows with the compression fittings P in the shell 12 Body connects.In the stationary state of the hydraulic press, cut down faster by leakage in the adjusting cavity 30 and described Pressure in pressure line 14, to which the hydraulic press is adjusted to by return spring 29 in maximum positive swept volume. When filling the adjusting cavity 30, the hydraulic press 10 is from maximum positive swept volume towards smaller positive swept volume toward backswing It is dynamic.In the filling of the lasting progress of the adjusting cavity 30, the hydraulic press 10 swings through zero swept volume, and backward Negative swept volume until being adjusted to maximum negative swept volume.
The valve gear 31 includes three 3/2 ratio road valves namely load-sensing regulating valve（LS regulating valves）40, pressure tune Save valve 39（The pressure-regulating valve is also referred to as hereinafter equipped with pressure-feed of reference numeral 45 together with the LS regulating valves 40 Throttle regulator, and the pressure-regulating valve is set to be located at the load pressure generally occurred within or more and high pressure accumulator 16 most In pressure more than big boost pressure）And it is configured to the control valve 48 of switching valve.The pressure-regulating valve 39 possesses first Connector, the connector can be connected by unloading circuit with storage tank 13.Second connector of the pressure-regulating valve 39 rests on described At compression fittings P.The third connector that can be connected with first connector or with the second connector passes through the pressure-feed stream The connector 46 of the adjusting cavity side of adjuster 45 can be connected with the adjusting cavity 30 at the regulating piston 26.LS regulating valves 40 First connector rests at the unloading circuit, and the second connector rests at the compression fittings P.The third of LS regulating valves 40 connects Head can be connected with its first or second connector and enduringly be connected with the first connector of the pressure-regulating valve 39.The pressure The pushing block of force regulating valve 39 not shown in further detail by compression spring adjusting cavity 30 and the LS regulating valves third connector Connection meaning in load, and loaded in the meaning that the adjusting cavity is connect with the compression fittings P by pump pressure. The pushing block of LS regulating valves 40 not shown in further detail in the third connector and first connector and thus with the unloading It is loaded by adjustment spring 41 in the meaning of the connection of circuit and by being present in the LS pressure of the LS connectors X and in third Connector is loaded with second connector and in the meaning that is thus connect with the compression fittings P.In the valve 40 At pushing block dominate have dynamic balance, when between the pump pressure and the LS pressure exist corresponding to the adjustment spring 41 power Difference when.In general, the difference is between 10 bar and 25 bar.This difference is also referred to as the pressure equivalent of adjustment spring or is known as pumping Δp.Currently, the pump Δ p may be calculated as 22 bar.
The LS pressure is the LS that the maximum load pressure in the consumable component 1 and 2 through actuating is either previously given simultaneously Control pressure.The maximum load pressure of the consumable component 1 and 2, which passes through, carries reversal valve of the reversal valve 54 as last chain link Chain is taken, and is reported into the common LS reporting lines 36 of this consumable component.In the maximum load of the consumable component 1 and 2 of hydraulic pressure Maximum pressure between pressure and previously given LS control pressures is selected to be reached by reversal valve 38, in the reversal valve First input end at there is the maximum load pressure of consumable component 1 and 2, the second input terminal of the reversal valve by LS valves 44 with The pressure line 14 can connect and the output end of the reversal valve connects with the LS at the pressure-feed throttle regulator 45 Head X is connected.It is disposed with nozzle between the second input terminal and the LS valves 44 of first reversal valve 38.Also this can be saved Nozzle.
In the base position of LS valves 44 pre-tightened by spring, the second input terminal of the reversal valve 38 is relative to pressure End and be connected with storage tank in line of force road 14.By the electromagnet energization to attraction, the LS valves 44 are trapped in on-position, In the on-position, the pressure of the pump circuit 14 is given the second input end of reversal valve 38 and works as this pressure ratio The output of this reversal valve is given when pressure higher at the first input end of the reversal valve 38.
Nozzle 64 is linked into from the LS of output end towards the pressure-feed throttle regulator 45 of the reversal valve 38 and connects In the LS reporting lines 56 of head X guidings.It, can between this nozzle and the LS connectors X of the pressure-feed throttle regulator 45 The pressure limit valve 62 of adjusting ratio is connected to the LS reporting lines 56, and the output end of the pressure limit valve is connected with storage tank. The pressure of the pressure limit valve is set by ratio electromagnet constantly in minimum value between such as maximum value of 300 bar It can change.The pressure limit valve 62 is such pressure limit valve：Its carry negative characteristic, pressure set points because And reduce with the increase of the energization of the electromagnet.By means of the nozzle 64 and the pressure limit valve 62, from presence In pump pressure in pressure line 14, LS control pressures can be generated into the LS reporting lines, the LS control pressures Less than the pump pressure.
The control valve is linked into the shell 12 of the pressure-feed throttle regulator 45 and the hydraulic press 10 in configuration aspects Between.It possesses the first connector 66, which is connected by circuit 67 with the section of the pump circuit 14, which deposits described Reservoir shut-off valve 22 is connected with the high pressure accumulator 16.Second connector of the control valve 48 and the pressure-feed stream tune The connector 46 for saving the adjusting cavity side of device 45 is connected.32 phase of chamber connector of the third connector of No. 3/2 valve and the adjusting cavity 30 Even.
In the base position of control valve 48 pre-tightened by spring, the connector 66 of the control valve 48 is ended.Institute The connector 46 for stating pressure-feed throttle regulator 45 is connected by control valve 48 with the chamber connector 32, to the pressure-feed Throttle regulator 45 can adjust the hydraulic press 10.It control valve 48 is switched to it connects by what is facilitated by the electromagnet attracted In logical position, the second connector of the pressure-feed throttle regulator 45 and thus connector 46 is ended, and high pressure storage Device 16 is connected with the chamber connector 32.
The valve 20,22,38,44,54,62 and 64 is combined stops valve block 52 to start.In addition, pressure sensor 75 （The memory pressure propped up and fitted in high pressure accumulator 16 is detected using the pressure sensor）With temperature sensor 76（Utilize this Temperature sensor detects the temperature of the pressure medium）Seat is placed at this valve block 52.
The control list that the startup function of the stopping function of the diesel motor 4 and the driving device of hydrostatic passes through electronics Member 80 controls, which is connected with the pressure sensor 75 by the circuit 81 of electricity, utilizes electric circuit 82 and band There is the electromagnet of pressure limit valve 62 to be connected, be connected with the component of the electricity at the diesel motor 4 using multiple circuits 83, with And it is connected with the valve 20,22,44 and 48 for capableing of electromagnetic actuation and with various other sensors using the circuit of other electricity.
For the diesel motor of operating, the valve 20,22,44 and 66 occupy in the accompanying drawings shown in position.The consumable component Thus shut-off valve 20 allows the consumable component 1 and 2 that the hydraulic pressure is supplied using pressure medium.The LS valves off-load leads to the storage Second input terminal of the reversal valve 38 of case, in the output of the reversal valve and thus in pressure-feed throttle regulator There is the consumable component 1 of the hydraulic pressure through actuating and 2 maximum load pressure at 45 LS connectors X.The pressure limit valve 62 electromagnet is so powered：So that the pressure limit valve is set on about 210 bar.The pressure limit valve 62 by The LS control pressures are limited to about 210 by this for the operation that the load-sensing-of the consumable component 1 and 2 of the hydraulic pressure is conditioned Bar is upper and the pump pressure of pump Δ p high 22 bar is limited on about 230 bar.The pressure limit is utilized as a result, Valve 62, the operation being conditioned for the load-sensing-of the consumable component 1 and 2 of the hydraulic pressure realize so-called pressure cut off.The control The connector 46 of the adjusting cavity side of the pressure-feed throttle regulator 45 is connected by valve processed with the adjusting cavity 30.It is overall as a result, On, in known manner so that being adjusted according to load-sensing, utilize the restriction of the pump pressure carried out by pressure limit valve 62, profit The consumable component 1 and 2 that the hydraulic pressure is supplied with pressure medium is feasible.Here, the high pressure accumulator passes through the memory Shut-off valve 22 and its return valve function are supercharged to pump pressure that is highest, occurring during the consumable component for actuating the hydraulic pressure On.
But this maximum pump pressure occurred due to by so-called second pressure limit that valve carries out for consumable component Pressure limit and less than for starting the memory pressure needed for the diesel motor.If situation thus is determined：The situation Show the disconnection of the diesel motor（Stop）, then there is such situation：Wherein, although not actuating the hydraulic pressure One of consumable component 1 and 2, but the diesel motor should then be closed the consumption first for other reasons without being turned off Part shut-off valve 20 and then the high pressure accumulator is pressurized on desired boost pressure.In addition, the LS valves 44 into Enter in on-position, in the on-position, the second input terminal of the reversal valve 38 is connected with the pressure line 14.It is described Pressure limit valve 62 is set to such pressure value by the controller 80 of electronics is by the corresponding energization of the electromagnet of subordinate On：The pressure value is located at through detected by the pressure sensor 75 and report with the pump Δ p to the controller Below 80 memory pressure.Due to nozzle 64, then it is set at the pressure at the pressure limit valve and is present in the pressure- At the LS connectors X of feed throttle regulator 45.From the pressure value of starting, pass through the electric current of the electromagnet by flowing at this time The reduction of ramped shaped gradually improves the setting pressure at the pressure limit valve 62.Existed by the setting pressure The degree of temporal change can set the volume flow of the hydraulic press 10 as pump work by the LS regulating valves Amount, the high pressure accumulator 16 is loaded using the volume flow.If desired memory pressure is, for example, 292 bar, Then the pressure set points of the pressure limit valve 62 do not continue to improve, when having reached 270 bar at this.The LS valves 44 It is again introduced into its resting position, which temporarily maximum can be powered, so as to by passing through internal leakage The nozzle do not drawn in Fig. 1 either accelerates in the LS report lines towards the abatement that carries out of flow control valve of storage tank Pressure abatement in road 56.
If the diesel motor is not switched off at this time, the hydraulic press 10 is so set in pump operation：So that The standby pressure of 22 bar is just also maintained in the pressure line 14, which is equal to pump Δ p.If had turned off Diesel motor, then the naturally described hydraulic press 10, which is detached from operation and is adjusted by the return spring 29, arrives maximum positive work appearance In product.The high pressure accumulator 16 is supercharged in maximum memory pressure, such as 292 bar.
If the diesel motor is again started up, the consumable component shut-off valve 20 and the control valve 48 are only actuated first. The latter enters in such position：Wherein, the adjusting cavity 30 is by the control valve 48 and the circuit 67 and the liquid Memory 16 is pressed to be connected.The adjusting cavity 30 thus loaded using memory pressure, to the hydraulic press from it is maximum just Swept volume is adjusted by zero swept volume towards maximum negative swept volume.Here, by the regulating piston 26 Power caused by memory pressure must only work against the power of the return spring 29, because existing in the adjusting cavity 33 The storage tank pressure fitted over by branch at the compression fittings P of the hydraulic press 10.Thus the adjusting especially rapidly carries out.
Only when the hydraulic press 10 has reached negative swept volume and thus ensure：The hydraulic press is not in motor It can be applied torsion moment on the internal combustion engine 4 against normal rotation direction in operation, especially when the hydraulic press is in When in maximum negative swept volume, the memory shut-off valve 22 enters in such position：Wherein, from hydraulic storage 16 Pressure medium flow towards the compression fittings P of the hydraulic press 10 is feasible.If the hydraulic press matches position sensor （The swept volume is detected using the position sensor）, then the memory shut-off valve 22 be able to rely on the position sensor Signal connect.In addition to this, it is connected at the rear of the control valve 48 to its certain period, ensures to reach by this period Negative swept volume, especially maximum negative swept volume.Pass through the consumable component shut-off valve 20 in its rest position, it is ensured that It is, it will not be inadvertently so that the movement of one of consumable component 1 and 2 of the hydraulic pressure.
After opening the memory shut-off valve 44, the hydraulic press 10 starts to drive the internal combustion as hydraulic motor Machine.Connecting the memory shut-off valve 44 shortly after, the pressure limit valve 62 is so manipulated by the controller 50：Make Obtain pressure（It is set in the pressure）With fixed pressure difference（In currently such as 35 bar）It is passed positioned at by the pressure Below memory pressure detected by sensor 75.Thus about described pump Δ p 1.6 times are so big for the pressure difference.Cause Declined by the pressure medium of the hydraulic press by taking out to flow for the memory pressure, thus is set at the pressure Pressure at power limit valve 62 also continuously reduces.Here to point out due to passing through 22 He of memory shut-off valve The pressure drop that the nozzle that may be structured between the memory shut-off valve and the hydraulic storage carries out, in the storage The pressure in track section between device shut-off valve 22 and the hydraulic press 10 is less than the memory pressure, and the pressure Drop with the internal combustion engine and thus the increase of the rotating speed of the hydraulic press and increase because flowing by the memory cut-off The pressure medium amount of valve increases.Pressure difference between memory pressure and the pressure being set at the pressure limit valve this When be chosen such that：So that the pressure for fitting over the compression fittings P of the hydraulic press 10 by branch is applied in the LS regulating valves Power, less than the summation of the power of the power and the adjustment spring 41 that are applied by the LS control pressures.The LS regulating valves 40 Therefore in position shown in the figure：In this position, the connector 46 is towards storage tank off-load.
As long as internal combustion engine, which reaches, starts rotating speed, 400 revolutions for example per minute（The internal combustion engine from the startup rotating speed Accelerating running is until idler revolutions in the case of not other driving device）, then the control valve 48 be again introduced into its basis In position and thus the adjusting cavity 30 detached with the hydraulic storage 16 and with the pressure-feed throttle regulator 45 Connector 46 be connected.Equally, from this moment, pressure value（The pressure limit valve 62 is set to just in the pressure value）No It is further continued for changing.Because the hydraulic press 10 is kept first in negative swept volume, then the pressure at the high pressure connection P Continue to be less than the memory pressure.In addition, the memory pressure declines and then the pump pressure also continues to decline. This, if the LS control pressures drop to value being set at the pressure limit valve 62 at this time and keeping constant or less （Because being less than the pressure set at the pressure limit valve 62 in the pressure of the input end of the LS valves 44）, then this holding Without the influence of the position to the LS regulating valves 40, because while the pressure being present at this valve described two at this time may About same size, but the position of the valve is maintained under the action of the adjustment spring 41.
After the control valve 48 enters in its base position, thus the adjusting cavity 30 passes through 48 He of control valve The LS regulating valves 40 are towards the storage tank off-load, and the back swing process of the hydraulic press can be immediately begun to.Institute It states in the adjusting cavity 33 at regulating piston 28, the pressure at the compression fittings P is fitted over there is branch.This pressure is together with return bullet Spring 29 works towards the direction that the stroke control element is adjusted towards the direction of zero swept volume.Because generally acting as Restoring force is very big, then the acceleration of the stroke control element is larger, to the reset of big dynamic implement.
Spacing in time after the control valve 48 returns in its base position（Ensure institute by the spacing Hydraulic press 10 is stated to adjust towards positive swept volume）In, the memory shut-off valve 22 is again introduced into its base position.Thus it protects Card, until during the entire reseting stage of zero swept volume, there is pressure in the pressure line 14.As a result, Avoid the hole at the hydraulic press.In addition, as described above, being acted at the stroke control element has Larger power.
When the hydraulic press 10 is back swung, from the hydraulic storage 16 towards the pressure medium flow of the hydraulic press It is continuously reduced, and is equal to zero in zero swept volume.Corresponding to this, between memory pressure and the pump pressure of hydraulic press 10 Pressure difference it is smaller and smaller and in zero swept volume be equal to zero.Until reaching startup rotating speed during starting process, depositing The pressure difference kept constant between reservoir pressure and the pressure being set at the pressure limit valve is chosen such that at this time： So that after the control valve 48 is back switched in base position, it is constantly maintained at this time at the pressure limit valve Pressure value the memory pressure is about located at hereinafter, reaching zero when the hydraulic press is in the reset with the pump Δ p When swept volume.It hereby is obtained that, the hydraulic press 10 is not adjusted in maximum positive swept volume, and is held in institute Such as percent 45 positive swept volume of maximum positive swept volume is stated hereinafter, the positive swept volume can make the diesel oil horse Up to static again.If when reaching zero swept volume, pump pressure and by setting pressure limit valve 62 by Difference between previously given LS control pressures is slightly less than the pump Δ p, then the hydraulic press 10 as pump smaller just Feed some amount when swept volume corresponds to the pump Δ p to be established between the pump pressure and the LS control pressures Difference.If when close to zero swept volume, pump pressure and by setting the pressure limit valve 62 it is previously given Difference between LS control pressures is slightly less than the pump Δ p, then the hydraulic press 10 as motor in smaller negative swept volume When also swallow some amount, to establish the difference for corresponding to the pump Δ p between the pump pressure and the LS control pressures.
Reach such state in any situation：Wherein, the hydraulic press 10 is lucky in small positive swept volume The so many pressure medium amount of feed：So that balance inside leakage and be maintained pump pressure, the pump pressure is with the pump Δ p More than previously given value by setting pressure limit valve 62.Next, the setting of the pressure limit valve 62 By being ramped down in almost zero pressure value, and correspondingly, the pump pressure is also reduced to lower standby pressure On.Accordingly, the consumable component shut-off valve 20 enters in its feed-through locations.
The driving device of hydrostatic according to the present invention especially also is suitable for using in specific structural scheme first In bus, rail vehicle or in the vehicle used in delivery service quotient namely in such vehicle：Usually utilizing should Vehicle stop and leave again.
Reference numeral list
1 hydraulic control device
2 other consumable component
4 diesel motors
6 bent axles
8 transmission shafts
10 hydraulic presses
12 shells
13 storage tanks
14 pressure lines
16 high pressure accumulators
18 branches
20 consumable component shut-off valves
22 memory shut-off valves
26 first regulating pistons
28 second regulating pistons
29 return springs
30 adjusting cavities
31 valve gears
32 chamber connectors
33 adjusting cavities
36 LS reporting lines
38 reversal valves
39 pressure-regulating valves
40 LS regulating valves
44 LS valves
45 pressure-feed throttle regulator
46 45 connector
48 control valves
52 start stopping valve block
54 reversal valves
56 LS reporting lines
62 pressure limit valves
64 nozzles
66 48 connector
67 circuits
75 pressure sensors
76 temperature sensors
80 control units
The circuit of 81 electricity
The circuit of 82 electricity
The circuit of 83 electricity
T storage tank connectors
P compression fittings
X LS connectors

Claims (12)

1. a kind of driving device of hydrostatic, which has hydraulic press（10）, the hydraulic press by means of hydraulic pressure tune Regulating device can be adjusted from maximum positive swept volume by zero swept volume to maximum in the swept volume of the hydraulic press Negative swept volume, the hydraulic press can be as pump operations and can be as motor using negative swept volume using positive swept volume Operation, the driving device have at least one high pressure accumulator（16）, for the operation as motor, from the high pressure accumulator It is middle to pass through in the hydraulic press（10）Compression fittings（P）With the high pressure accumulator（16）Between the pressure line that moves towards（14）Energy Enough pressure medium is utilized to supply the hydraulic press（10）, the driving device is with the storage with first position and the second position Device shut-off valve（22）, which is arranged in the pressure line（14）In and made by the memory shut-off valve From the high pressure accumulator（16）Towards hydraulic press（10）The portion that fluidly connects opened in the first position and described End in the second position, and the driving device has the control unit of electronics（80）, depend on the signal of the control unit The memory shut-off valve can be operated（22）, which is characterized in that by hydraulic press（10）From negative swept volume towards positive work When volume adjustment, the control unit of the electronics（80）It is provided at this time for by the memory shut-off valve（22）From first position The signal being switched in the second position so that the memory shut-off valve（22）In the hydraulic press（10）Zero swept volume or It is just switched in the second position in the case of the positive swept volume of person.
2. the driving device of hydrostatic described in accordance with the claim 1, wherein the regulating device includes being abutted to first Regulating piston（26）The first adjusting cavity（30）, be abutted to the second regulating piston（28）The second adjusting cavity（33）With return bullet Spring（29）, the direction of the return spring towards maximum positive swept volume is worked, for first adjusting cavity, is passed through Valve gear（31）Can control the influent stream for the pressure medium for facilitating the direction towards maximum negative swept volume to be adjusted and Can control drainage, second adjusting cavity constantly with the compression fittings（P）It fluidly connects and second adjusting cavity exists Towards reduction in the adjusting in the direction of maximum negative swept volume and in the adjusting in the direction towards maximum positive swept volume Middle increase.
3. the driving device of hydrostatic according to claim 2, wherein the valve gear（31）Including control valve （48）, by the control valve, independent of compression fittings（P）, from pressure medium source（16）In can utilize pressure medium for The hydraulic press（10）It is supplied, for towards the first adjusting cavity（30）Negative swept volume adjust.
4. the driving device of hydrostatic described in accordance with the claim 3, wherein the valve gear（31）For the hydraulic press （10）As for the operation of pump include carry connector（46）Hydraulic pressure adjuster（45）, wherein the control valve（48）It is No. 3/2 valve, the control valve carry the first connector, the adjuster of first connector and the hydraulic pressure（45）Connector（46）Fluid connects It connects, and the control valve carries the second connector（66）, second connector and the pressure medium source（16）It fluidly connects, and should Control valve carries third connector, the third connector and first adjusting cavity（30）It is connected, and wherein, the control valve（48） With first position, in the first position, the third connector and the first connector fluidly connects and the second connector（66）Quilt Cut-off, and the control valve has the second position, in the second position, the third connector and the second connector（66）It is connected And first connector is ended.
5. the driving device of hydrostatic according to claim 4, wherein the adjuster of the hydraulic pressure（45）Including load Induction（LS）Regulating valve（40）, the load-sensing（LS）Regulating valve flows to the first adjusting cavity of the regulating device in pressure medium （30）Meaning in by the compression fittings（P）The pressure-loaded at place, and in pressure medium from first adjusting cavity （30）By adjustment spring in the meaning of middle outflow（41）Be present in LS connectors（X）The LS control pressures at place load, and wherein, In the hydraulic press（10）Negative swept volume in the case of also LS control pressures are given to the load-sensing（LS）It adjusts Valve（40）LS connectors（X）.
6. the driving device of hydrostatic according to claim 5, wherein in the control valve（48）It is also located at the control When in the second position of valve, the load-sensing is loaded using LS control pressures（LS）Regulating valve（40）.
7. according to the driving device of hydrostatic described in claim 5 or 6, wherein when the hydraulic press（10）In past backswing When reaching zero swept volume from maximum negative swept volume when dynamic, it is given to the LS connectors（X）The LS control pressures About with adjustment spring（41）Pressure equivalent and less than in the compression fittings（P）The pressure at place, to the hydraulic press （10）Be conditioned by zero swept volume, but simultaneously non-regulated until maximum positive swept volume.
8. according to the driving device of hydrostatic described in claim 5 or 6, wherein when the control valve（48）It is also located at this When in the second position of control valve, LS control pressures have been given to the load-sensing（LS）Regulating valve（40）LS connectors （X）, wherein the LS control pressures are first with fixed pressure difference, in the high pressure accumulator（16）In pressure hereinafter, with With the memory pressure of decline, and wherein, when the control valve（48）It is converted from the second position of the control valve to the control When in the first position of valve, the LS control pressures are kept constant.
9. the driving device of hydrostatic according to claim 8, wherein the fixed pressure difference is about described negative Carry induction（LS）The adjustment spring of regulating valve（41）It is 1.6 times of pressure equivalent so big.
10. according to the driving device of hydrostatic described in claim 5 or 6, wherein the hydraulic press holds with work is useful for Long-pending logger, and wherein, after control valve is switched to from the second position in first position, the LS control pressures Size depends on the change of the size or negative swept volume of negative swept volume to determine.
11. according to the driving device of hydrostatic according to any one of claims 1 to 6, wherein the hydraulic press is with useful In the logger of swept volume, and wherein, after control valve is switched to from the second position in first position, the storage Device shut-off valve is switched to from first position in the second position dependent on the size of detected swept volume.
12. according to the driving device of hydrostatic according to any one of claims 1 to 6, the driving device is in starting Combustion engine（4）.
CN201580049475.2A 2014-09-15 2015-08-04 The driving device of hydrostatic Active CN106715925B (en)

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DE102014218419.3 2014-09-15
DE102014218419.3A DE102014218419A1 (en) 2014-09-15 2014-09-15 Hydrostatic drive
PCT/EP2015/067919 WO2016041685A1 (en) 2014-09-15 2015-08-04 Hydrostatic drive

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CN106715925A (en) 2017-05-24
EP3194758A1 (en) 2017-07-26
DE102014218419A1 (en) 2016-03-17
WO2016041685A1 (en) 2016-03-24
EP3194758B1 (en) 2018-10-24
US20170254308A1 (en) 2017-09-07

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